EP1746288A2 - Ensemble moteur-pompe - Google Patents

Ensemble moteur-pompe Download PDF

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Publication number
EP1746288A2
EP1746288A2 EP06123309A EP06123309A EP1746288A2 EP 1746288 A2 EP1746288 A2 EP 1746288A2 EP 06123309 A EP06123309 A EP 06123309A EP 06123309 A EP06123309 A EP 06123309A EP 1746288 A2 EP1746288 A2 EP 1746288A2
Authority
EP
European Patent Office
Prior art keywords
bearing
motor
channel
pump unit
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06123309A
Other languages
German (de)
English (en)
Other versions
EP1746288A3 (fr
Inventor
Thomas Bartsch
Dieter Dinkel
Sven Martin
Rüdiger BRIESEWITZ
Axel Niescher
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of EP1746288A2 publication Critical patent/EP1746288A2/fr
Publication of EP1746288A3 publication Critical patent/EP1746288A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B60T8/368—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, master cylinders
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4031—Pump units characterised by their construction or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0443—Draining of the housing; Arrangements for handling leaked fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/006—Crankshafts

Definitions

  • the present invention relates to a motor-pump unit for a motor vehicle brake system, comprising a motor and a pump, which comprises a shaft driven by the motor, the shaft end of which is rotatably mounted in a receiving body provided with valves and connecting channels with at least one bearing, wherein the shaft drives displacement means that extend into a crankcase, and wherein the bearing is provided in front of a bearing plate of the engine between the crankcase and bearing plate.
  • Such a motor-pump unit is basically known.
  • the filling of a motor vehicle brake system with the required pressure medium after assembly of the individual system components such as in particular a master cylinder, a pipe and hose system, the motor-pump unit and wheel brakes at the vehicle manufacturer.
  • the entire brake system is evacuated in a first method step in order to supply the intended pressure medium in a second method step.
  • roller bearing assemblies of motor-pump units are exposed to high, as well as non-rolling stresses, especially during the Druckstoffbehellprozeß.
  • sealed bearings for example, to Ausknöpfen of sealing elements such as sealing lips.
  • the bearings fail prematurely, which is particularly problematic in brake systems with high pump running times, in particular electro-hydraulic brake systems.
  • Unsealed bearings have free access to the rolling surfaces, and do not allow the use of a special lubricant. This is problematic if the lubricating properties of the pressure medium used are insufficient or if the pressure medium contains wear products which can cause tread damage.
  • the invention is based on the object of providing an improved motor-pump assembly in which the risk of bearing damage and lubricant leaching from bearings is reduced.
  • a channel is provided, which connects a side facing away from the crank chamber of the bearing with a leakage drainage channel for the crankcase.
  • An advantageous embodiment of the embodiment has a channel which is provided in the receiving body.
  • the recordable leakage volume is further increased by opening the channel into a chamber bounded by the bearing shield and the receiving body, the chamber being connected to the leakage drainage channel.
  • a motor-pump unit 1 for use in a motor vehicle brake system is connected on the one hand to wheel brakes, not shown, and on the other hand to a donor, not shown, such as a master cylinder with a pressure medium reservoir.
  • a receiving body 2 has at least six hydraulic connections.
  • the unit is particularly suitable and intended for electro-hydraulic brake systems, which have a, on or in the receiving body 2 integrated high-pressure accumulator, which serves to feed the wheel brakes.
  • the master cylinder is here only in Emergency used for the brake application and serves primarily to simulate brake actuation forces.
  • the motor-pump unit 1 further includes a pump 3 for supplying the high-pressure accumulator or for supplying wheel brakes and a motor 4 for driving the pump 3.
  • An electronic unit 14 for controlling and regulating the system is located on a, the motor 4 opposite side the receiving body 2, wherein electronic control and supply lines of the motor 4 are passed through the receiving body 3.
  • the motor 4 drives a pump shaft 5 which is rotatably disposed within a stepped through-hole 6 by means of sealed bearings 7, 8.
  • Bearing 7 is designed as a fixed bearing, while bearing 8 is designed as a floating bearing, and therefore can not absorb axial forces.
  • the pump shaft 5 acts on displacement means for the pressure medium. In the illustrated, preferred embodiment, it is a radial piston pump which has as a displacement means via pump piston 9,10, which open into an approximately centered between the bearings 7,8 arranged space 11, and by an eccentric connected to the shaft (not graphically shown) are driven.
  • the number of pump pistons is in principle arbitrary, with 3 pistons being preferred because this reduces pulsations and noise.
  • a roller bearing 12 In order, for example, to provide pressure medium, which has accumulated in the chamber 11 as a result of internal leakage, to the system again (or if the space 11 is already flooded with pressure medium), a channel opens into the space 11 13, which communicates with the pressure fluid reservoir.
  • a motor facing away shaft end 15 extends into a space 16 and passes through a bottom 17 which is inserted into the through hole 6, and rests axially on an outer ring of the bearing 8. Between shaft 5 and a through hole through the bottom 17 is a gap for the passage of pressure medium.
  • connection 19 is designed as a channel 20, wherein its wall consists of peripheral regions of the inner ring and bearing seat.
  • the bearing seat 18 has a flattening 21, while the inner ring is unchanged annular, so that there is a crescent-shaped, free channel cross-section for pneumatic evacuation and the pressure medium passage between these adjacent components.
  • Eccentricity and channel 20 are arranged in alignment with each other for an unchanged good bearing seat in the axial direction, as is apparent from Fig. 2.
  • the flattening 21 is substantially in the same angular position as the Exzentermaximum (maximum stroke), as illustrated by a dashed line in Fig. 2. Because the maximum bearing forces are removed in the displacement stroke on the opposite side of the Exzentermaximum (from the perspective of the bearing inner ring), despite channel 20 no reduction of the effective, force-transmitting surface on the bearing seat. Bearing seat damage is excluded.
  • the flattening 21 can be replaced in principle by holes are provided which extend through the shaft interior.
  • the free space 16 is provided with a lid 22 formed as a closure, which prevents loss of pressure medium on the side of the electronic unit 14.
  • the cover is placed on a bore step 23 of the through hole 6 and caulked with the receiving body 2 liquid and gas-tight.
  • a sealing element 25 is provided between eccentric and bearing 7 in the region of the motor-side shaft end 24, which is arranged in a holding body 26, so that no leakage fluid can escape from the receiving body 2 in the direction of motor 4.
  • FIG. 3 is a flying bearing with a cantilevered shaft end removed.
  • Such flying bearing is widely used in engine-pump assemblies of vehicle brake systems.
  • the known constructions suffer from the disadvantage that alternating heating and cooling processes - in particular of the engine - can to a certain extent cause a suction, so that leakage fluid, which is located in the crank chamber, can pass as a result of a pressure difference in the engine compartment. Damage to the bearing lubricant filling or lubricant flushing as well as damage to the bearing sealant is possible.
  • the pump drive is a pump shaft 5 with an eccentric, which is arranged in the crank chamber 11.
  • a sealed bearing 7 which in front of a bearing plate 30 of the motor 4 between Crank 11 and end plate 30 is provided.
  • the bearing plate 30 is formed of plastic material, closes the pot-shaped motor housing and carries the sealed bearing 7 before the final assembly of motor 4 and receiving body 2 provisionally by a ring nozzle 31 surrounds a part of the bearing outer ring.
  • the crank chamber 11 is connected to a leakage drainage channel 32, which accumulate accumulated leakage fluid in a storage chamber 33 of the unit 1, stockpile, or for example can be discharged into the environment.
  • the receiving body 2 may have a tube 34 which extends into the storage chamber 33, wherein an outlet opening of the Tube 34 is arranged at a distance from the free liquid level.
  • the crankraumabgewandte side of the bearing 7 via one or a plurality of channels 13 connected to the leakage drainage channel 32.
  • the annular nozzle 31 has one or more channels 13, which extend in the direction of the crank chamber facing away from the bearing seat in the bearing plate 30, so that contact with the gap 35 can be produced, extending between a bulkhead of the bearing plate 30 and the side facing away from the crank of the bearing 7 is located.
  • Each channel 13 connects them Side facing away from the crankcase with the leakage drainage channel 32, which leakage fluid - which can accumulate in the crank chamber 11 and the gap 35 - either in the environment or in the storage chamber 33 derived. Due to the described features, the motor interior is protected in the region of the shaft outlet against the ingress of leakage fluid. Even if leakage fluid should pass through the bearing 7, this can be supplied to the already provided leakage circuit.
  • the system and in particular the bearing 7 is depressurized under pneumatic aspects by the connection to the ambient atmosphere. This prevents leakage fluid or ambient fluid from being forced under the action of a pressure gradient through the bearing 7 into the interior of the engine. It is also prevented that sealing discs of the bearing 7 can ausknumblen under the action of a pressure gradient.
  • the channel 13 may in principle be provided as a partial recess in the receiving body 2, as is apparent from Fig. 3. In principle, the channel 13 may also be provided on a bearing outer ring, but this requires a separate processing of this standardized component. In a not shown, modified embodiment, the channels 13 are provided in the receiving body 2.
  • the channel 13 does not have to open directly into the leakage drainage channel 32.
  • a chamber which is bounded by the end plate 30 and the receiving body 2.
  • the invention allows for extremely compact design a much improved protection of the motor. 4 against leakage fluid while avoiding residues of water and / or leakage fluid (brake fluid) within the unit.
  • the invention is applicable to a variety of pump types having so-called internal leakage.
  • the invention is in principle also suitable for use in conjunction with a gear pump, which has, for example, internal gear pairs as displacement means.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Electromagnetism (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP06123309A 2002-11-11 2003-11-06 Ensemble moteur-pompe Withdrawn EP1746288A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10252622A DE10252622A1 (de) 2002-11-11 2002-11-11 Motor-Pumpen-Aggregat
EP03810968A EP1563188A1 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP03810968A Division EP1563188A1 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Publications (2)

Publication Number Publication Date
EP1746288A2 true EP1746288A2 (fr) 2007-01-24
EP1746288A3 EP1746288A3 (fr) 2009-03-04

Family

ID=32185540

Family Applications (2)

Application Number Title Priority Date Filing Date
EP03810968A Withdrawn EP1563188A1 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe
EP06123309A Withdrawn EP1746288A3 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP03810968A Withdrawn EP1563188A1 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Country Status (5)

Country Link
US (1) US7293495B2 (fr)
EP (2) EP1563188A1 (fr)
JP (2) JP2006505743A (fr)
DE (1) DE10252622A1 (fr)
WO (1) WO2004044427A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009132994A1 (fr) * 2008-04-28 2009-11-05 Continental Teves Ag & Co. Ohg Groupe hydraulique
WO2009138339A1 (fr) * 2008-05-15 2009-11-19 Continental Teves Ag & Co. Ohg Groupe hydraulique

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4267557B2 (ja) * 2004-10-29 2009-05-27 トヨタ自動車株式会社 ころ軸受およびそれを内蔵したポンプ
US20090263258A1 (en) * 2007-02-27 2009-10-22 Sauer-Danfoss Inc. Vibration dampening media in hydraulic power units
US20100047088A1 (en) * 2008-08-20 2010-02-25 Protonex Technology Corporation Roller vane pump with integrated motor
US20100047097A1 (en) * 2008-08-20 2010-02-25 Protonex Technology Corporation Roller vane pump with integrated motor
JP5353139B2 (ja) * 2008-09-17 2013-11-27 株式会社アドヴィックス ブレーキ圧制御装置
JP5719213B2 (ja) * 2011-03-30 2015-05-13 株式会社ケーヒン 圧縮機
DE102011085288A1 (de) * 2011-10-27 2013-05-02 Continental Teves Ag & Co. Ohg Hydraulikaggregat
JP6395149B2 (ja) * 2014-08-04 2018-09-26 日立オートモティブシステムズ株式会社 ブレーキ液圧制御装置
DE102015222286A1 (de) * 2015-11-12 2017-05-18 Robert Bosch Gmbh Hydraulikblock und Hydraulikaggregat
PL3453101T3 (pl) 2016-05-04 2021-09-20 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Sposób wytwarzania obudowy bieguna
JP6876323B2 (ja) * 2017-02-03 2021-05-26 応研精工株式会社 モーター付きポンプ
TWI632305B (zh) * 2017-10-13 2018-08-11 建準電機工業股份有限公司 軸承組及具軸承組之馬達
IT201800009042A1 (it) * 2018-10-01 2020-04-01 Lyra Bearing Srl “pompa migliorata”

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2296296A (en) * 1994-12-20 1996-06-26 Bosch Gmbh Robert Piston pump
WO1997048583A1 (fr) * 1996-06-18 1997-12-24 Itt Manufacturing Enterprises, Inc. Pompe a piston radial
EP1041700A2 (fr) * 1999-03-29 2000-10-04 Continental Teves AG & Co. oHG Organe entrainé par moteur
WO2001040042A1 (fr) * 1999-12-01 2001-06-07 Continental Teves Ag & Co. Ohg Unite hydraulique

Family Cites Families (14)

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Publication number Priority date Publication date Assignee Title
JPS59160870U (ja) * 1983-04-15 1984-10-27 トヨタ自動車株式会社 ポンプの軸支持装置
JPS6228522A (ja) * 1985-07-29 1987-02-06 Aisin Seiki Co Ltd 流体機器の軸受構造
AT394892B (de) * 1989-09-18 1992-07-10 Tech Hydraulikgeraete Ges M B Radialkolbenpumpe
DE4241827A1 (de) * 1992-12-11 1994-06-16 Teves Gmbh Alfred Geräuschreduziertes Pumpenaggregat, insbesondere für geregelte Bremsanlagen
DE4433972A1 (de) * 1994-09-23 1996-03-28 Teves Gmbh Alfred Elektromotor, Pumpe sowie ein Elektromotor/Pumpenaggregat
DE19633170A1 (de) * 1996-08-17 1998-02-19 Teves Gmbh Alfred Eelektromotor-/Pumpenaggregat
JPH11103559A (ja) * 1997-09-26 1999-04-13 Aisin Seiki Co Ltd 駆動装置
JP2002520221A (ja) * 1998-07-16 2002-07-09 コンティネンタル・テーベス・アクチエンゲゼルシヤフト・ウント・コンパニー・オッフェネ・ハンデルスゲゼルシヤフト 液圧装置
DE19922297A1 (de) 1999-05-14 2000-11-16 Bosch Gmbh Robert Pumpeneinheit
DE19927658A1 (de) * 1999-06-17 2000-12-21 Bosch Gmbh Robert Pumpenaggregat
EP1353067B1 (fr) * 1999-10-25 2009-08-05 Continental Teves AG & Co. oHG Groupe moto-pompe
DE10023947A1 (de) * 2000-05-16 2001-11-22 Bosch Gmbh Robert Wälzlager, Kolbenpumpe und Pumpenaggregat
DE10045619C1 (de) * 2000-09-15 2002-05-29 Bosch Gmbh Robert Werkzeugmaschine mit einem Raum mit Schmiermittel und einer Druckausgleichseinrichtung des Raums
JP2004521794A (ja) * 2001-02-02 2004-07-22 コンティネンタル・テーベス・アクチエンゲゼルシヤフト・ウント・コンパニー・オッフェネ・ハンデルスゲゼルシヤフト 電子制御式ブレーキ装置用ユニット

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2296296A (en) * 1994-12-20 1996-06-26 Bosch Gmbh Robert Piston pump
WO1997048583A1 (fr) * 1996-06-18 1997-12-24 Itt Manufacturing Enterprises, Inc. Pompe a piston radial
EP1041700A2 (fr) * 1999-03-29 2000-10-04 Continental Teves AG & Co. oHG Organe entrainé par moteur
WO2001040042A1 (fr) * 1999-12-01 2001-06-07 Continental Teves Ag & Co. Ohg Unite hydraulique

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009132994A1 (fr) * 2008-04-28 2009-11-05 Continental Teves Ag & Co. Ohg Groupe hydraulique
US8702182B2 (en) 2008-04-28 2014-04-22 Continental Teves Ag & Co. Ohg Hydraulic unit
WO2009138339A1 (fr) * 2008-05-15 2009-11-19 Continental Teves Ag & Co. Ohg Groupe hydraulique
US8500218B2 (en) 2008-05-15 2013-08-06 Continental Teves Ag & Co. Ohg Hydraulic system

Also Published As

Publication number Publication date
EP1563188A1 (fr) 2005-08-17
WO2004044427A1 (fr) 2004-05-27
DE10252622A1 (de) 2004-05-27
US20060056995A1 (en) 2006-03-16
JP2011058499A (ja) 2011-03-24
JP5431279B2 (ja) 2014-03-05
EP1746288A3 (fr) 2009-03-04
JP2006505743A (ja) 2006-02-16
US7293495B2 (en) 2007-11-13

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Effective date: 20090711